EP3708804A1 - Laufradspitzenhohlraum - Google Patents

Laufradspitzenhohlraum Download PDF

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Publication number
EP3708804A1
EP3708804A1 EP20163432.6A EP20163432A EP3708804A1 EP 3708804 A1 EP3708804 A1 EP 3708804A1 EP 20163432 A EP20163432 A EP 20163432A EP 3708804 A1 EP3708804 A1 EP 3708804A1
Authority
EP
European Patent Office
Prior art keywords
impeller
cavity
flow passage
side opening
main flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP20163432.6A
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English (en)
French (fr)
Inventor
Hien Duong
Jason Nichols
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pratt and Whitney Canada Corp
Original Assignee
Pratt and Whitney Canada Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pratt and Whitney Canada Corp filed Critical Pratt and Whitney Canada Corp
Publication of EP3708804A1 publication Critical patent/EP3708804A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
    • F02C3/08—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor the compressor comprising at least one radial stage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/06—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output providing compressed gas
    • F02C6/08—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output providing compressed gas the gas being bled from the gas-turbine compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • the present invention relates generally to centrifugal compressors, and more particularly to impellers with diffusers.
  • Centrifugal compressors include an impeller and a diffuser downstream therefrom. Pressure at impeller exit may vary circumferentially due to pressure difference between pressure/suction sides of the impeller blades, and due to the turbulent nature of the flow as it travels downstream, especially after the bend area of the impeller. This may set up a circumferentially varying pattern of flow distortion that may degrade performance of both upstream impeller and downstream diffuser, which is undesirable.
  • a gas turbine engine for an aircraft comprising: a centrifugal compressor including an impeller with impeller blades extending from a hub and a diffuser downstream of the impeller, the impeller mounted for rotation about a central longitudinal axis within an outer shroud, a main flow passage extending between the hub and the shroud to an impeller exit defined downstream of the impeller blades, and a cavity disposed adjacent the exit, the cavity communicating with the main flow passage via at least one aperture through a main flow passage wall from an impeller-side opening to a cavity-side opening, the impeller-side opening located radially outward from the impeller exit relative to the central longitudinal axis, and the cavity-side opening located closer to the central axis than the impeller-side opening.
  • the gas turbine engine as defined herein may also include, in whole or in part and in any combination, one or more of the following features:
  • a gas turbine engine for an aircraft comprising: a centrifugal compressor having a main flow passage defined therethrough, the centrifugal compressor including: an impeller with impeller blades extending from a hub, the impeller mounted for rotation about a central longitudinal axis within an outer shroud, the impeller having a shroud side facing the outer shroud and an axially opposed hub side, an impeller exit defined downstream of the impeller blades; a main flow passage wall located on the shroud side near the impeller exit, the main flow passage wall separating a cavity disposed on the shroud side from the main flow passage; and one or more apertures defined through the main flow passage wall and extending along a respective aperture axis between the cavity and the main flow passage, the one or more apertures having a respective main flow passage side opening located radially outward from the impeller exit relative to the central longitudinal axis, the aperture axis disposed at a radial angle relative to the central longitudinal axis when viewed in a me
  • the gas turbine as defined herein may also include, in whole or in part and in any combination, one or more of the following features:
  • a method for operating a centrifugal compressor of a gas turbine engine comprising: providing bidirectional flow communication between a cavity located on a shroud side of the impeller, on one side of a main flow passage wall, the main flow passage wall separating the cavity from the main flow passage and located adjacent an impeller exit, wherein bidirectional flow communication is provided via one or more apertures defined through the main flow passage wall and extending along a respective aperture axis between the cavity and the main flow passage, the one or more apertures having a respective main flow passage side opening located radially outward relative to the impeller exit relative to the central longitudinal axis, the aperture axes disposed at a radial angle relative to the central longitudinal axis when viewed in a meridional plane of the centrifugal compressor.
  • Fig. 1 illustrates an exemplary gas turbine engine 10 of a type preferably provided for use in subsonic flight.
  • the exemplary gas turbine engine 10 as shown is a turbofan, generally comprising in serial flow communication a fan 12 through which ambient air is propelled, a compressor section 14 for pressurizing the air, a combustor 16 in which the compressed air is mixed with fuel and ignited for generating an annular stream of hot combustion gases, and a turbine section 18 for extracting energy from the combustion gases. Also shown is a central longitudinal axis 11 of the engine 10.
  • turbofan engine As an example, it is understood that aspects of the present disclosure may be equally applicable to other types of combustion engines in general, and other types of gas turbine engines in particularly, including but not limited to turboshaft and turboprop turbine engines, auxiliary power units (APU), and the like.
  • APU auxiliary power units
  • the compressor section 14 of the engine 10 includes one or more compressor stages, at least one of which includes a centrifugal compressor 14A.
  • the centrifugal compressor 14A has a main flow passage defined therethrough and includes a rotating impeller 15 and a downstream diffuser 20.
  • the impeller 15 is mounted for rotation within an outer shroud 19 about the central longitudinal axis 11.
  • the impeller 15 may draw air axially, and rotation of the impeller 15 may increase the velocity and build pressure within a main gas flow as the main gas flow is directed though the diffuser 20, to flow out in a radially outward direction under centrifugal forces.
  • the diffuser 20 is positioned immediately downstream of the exit of a rotating component of the compressor, which in the exemplary embodiment is the impeller 15.
  • the diffuser 20 may form a fluid connection between the impeller 15 and the combustor 16, thereby allowing the impeller 15 to be in serial flow communication with the combustor 16.
  • the diffuser 20 may redirect the radial flow of the main gas flow exiting the impeller 15 to an annular axial flow for presentation to the combustor 16.
  • the diffuser 20 may include vanes (not shown) downstream of the impeller exit by which the radial flow leaving the impeller 15 may exit the diffuser 20 and be led toward the next compressor stage or to the combustor 16.
  • the diffuser may include one or more fishtail diffuser pipes directing the flow downstream of the impeller 15 to exit the diffuser 20.
  • the diffuser 20, with or without vanes, may also reduce the velocity and increase the static pressure of the main gas flow when it is directed therethrough.
  • the diffuser 20 includes an annular diffuser body 22 mounted about the impeller 15.
  • the diffuser body 22 forms the corpus of the diffuser 20 and provides the structural support required to resist the loads generated during operation of the centrifugal compressor 14A.
  • the diffuser body 22 forms an annular diffuser ring extending circumferentially about the impeller exit 15B, and may have a vaned, vane-less, or semi-vaned space.
  • the diffuser body 22 is mounted about a circumference of the compressor or impeller exit 15B so as to receive the main gas flow therefrom.
  • the impeller 15 includes impeller blades 15A extending from an impeller hub and having an axial bend extending radially outwardly with respect to the central longitudinal axis 11, which allow the axial main gas flow upstream of the impeller 15 to be directed radially outwardly away from the central longitudinal axis 11.
  • the impeller 15 defines a shroud side, which corresponds to a region of the impeller 15 circumferentially surrounding the impeller blades 15A, and an opposed hub side, which is located downstream of the impeller 15, at the impeller back plate side.
  • Fig. 2 shows a shroud side and an opposed hub side, respectively shown on the left side and right side of the illustrated example of centrifugal compressor 14A.
  • the impeller blades 15A each have a pressure side and a suction side, named as such with reference to the pressure differential between the gas flow pressure to the fore of the blades 15A versus the aft of the blades 15A caused by rotation of the impeller 15 and fluid interaction with the main gas flow.
  • This may set up a circumferentially varying pattern of flow distortion at the impeller exit 15B, which is defined downstream of the impeller blades 15A, in other words at the exducer of the impeller 15 adjacent the tip of the impeller 15, or more specifically the tip of the blades 15A of the impeller 15.
  • a pressure differential may occur between the pressure side and the suction side of the impeller blades 15A.
  • the pressure at impeller exit 15B may vary circumferentially due to a pressure difference between the pressure side and the suction side of the impeller blades 15A during rotation. This may create flow turbulence of the main gas flow travelling through the impeller 15, which may build along the impeller blades 15A, and more particularly after the bend area 15C of the blades 15A. This flow distortion may degrade performance of the gas turbine engine 10 as a whole and/or more specifically upstream of the impeller 15 and downstream of the diffuser 20.
  • a cavity 30 is disposed on the shroud side of the impeller 15, on one side of a main flow passage wall separating the main flow passage from the cavity 30, where the main flow passage wall is located adjacent the impeller exit 15B.
  • the cavity 30 may be circumscribed by the annular ring and an adjacent portion of the outer shroud 19.
  • the diffuser body 22 defines a radially outward peripheral wall of the cavity 30, and the outer shroud 19 defines a radially inward peripheral wall of the cavity 30.
  • the cavity 30 may be an internal cavity defined solely in the diffuser body 22 and/or in the outer shroud 19.
  • the cavity 30 may have any suitable internal volume and/or shape.
  • the cavity 30 is in fluid communication with the main flow passage exiting the impeller 15, in other words at the impeller exit 15B, via at least one (i.e. one or more) apertures 32, as will be seen. Flow enters and exits the cavity 30 via the same flow passage(s) defined through the one or more apertures 32, which in the present embodiment comprise a series of apertures 32 defined through the main flow passage wall and extending between the cavity and the main flow passage.
  • the cavity 30 is an annular chamber that is closed but for the apertures 32, such that the apertures 32 provide the sole fluid connection to the closed chamber. This may be different in other embodiments, where, for instance, the cavity 30 may be in fluid communication with other parts of the engine 10 as well, via bleed off-take(s), if desirable.
  • the apertures 32 are circumferentially equally spaced apart about the impeller 15. This may be different in other embodiments, where, for instance, the apertures 32 may be unevenly distributed along the circumference of the impeller 15.
  • the centrifugal compressor 14A includes a number of apertures 32 at least more than half the number of impeller blades 15A (rounded up), including the blades 15A within an exducer portion and extending to the impeller exit 15B. This may balance the flow exchange between the cavity 30 and the main flow passage between the suction side of a blade 15A and the opposite pressure side of an adjacent one of the blades 15A over the circumference of the impeller 15.
  • the series of apertures 32 are defined at an interface between the outer shroud 19 and the diffuser body 22.
  • the outer shroud 19 and the diffuser body 22 mate at a common edge, where they contact each other between circumferentially adjacent apertures 32.
  • the common edge of the outer shroud 19 and the diffuser body 22 form respective radially inward and radially outward wall of the apertures 32.
  • the series of apertures 32 are defined through a portion of the diffuser body 22, and provide fluid communication between the main flow passage at the impeller exit 15B and the cavity 30.
  • the main flow passage wall through which the apertures 32 are defined is part of the diffuser body 22.
  • the series of apertures 32 are defined through a portion of the outer shroud 19.
  • the main flow passage wall through which the apertures 32 are defined is part of the outer shroud 19. This may depend on the location of the cavity 30 (within the shroud 19 or within the diffuser body 22).
  • the apertures 32 are located downstream of the impeller 15, adjacent the impeller exit 15B.
  • the apertures 32 allow bidirectional flow communication between the cavity 30 and the main flow passage at the tip of the impeller blades 15A.
  • flow may enter and exit the cavity via the apertures 32 in an alternating sequence as the impeller 15 rotates. More particularly, as the impeller 15 rotates, a portion of the fluid of the main flow passage at the impeller exit 15B enters the cavity 30 and reduces in velocity.
  • the pressure field inside the cavity 30 may thus be different than that of the flow just outside the cavity 30. This pressure difference drives the flow in and out the cavity 30.
  • This bidirectional flow cycle entering and leaving the cavity 30 may thus continue so long as the impeller 15 rotates and generate sufficient pressure differential between the pressure side and suction side of the blades 15A to provide such flow distortion.
  • a constant momentum exchange between the fluid inside the cavity 30 and the main flow passage occurs during operation.
  • the flow condition into the diffuser 20 downstream the impeller exit 15B has a more uniform flow stream. Circumferential/axial flow distortions originating from the impeller 15 are therefore damped before flowing through the diffuser 20.
  • the centrifugal compressor 14A of the gas turbine engine 10 which has the impeller 15 that rotates within the outer shroud 19 about the longitudinal axis 11, has a bidirectional flow communication provided between the cavity 30 located on a shroud side of the impeller 15 and a main flow passage at the impeller exit 15B via the series of apertures 32 extending between the cavity 30 and the main flow passage at the impeller exit 15B.
  • the apertures 32 have their aperture axis 32A at a radial angle when viewed in a meridional plane of the centrifugal compressor 14A relative to the central longitudinal axis 11.
  • the fluid flowing out from the cavity 30 via the apertures 32 may have a radial component relative to the main flow passage, which may reduce flow mixing losses and help reducing the flow distortion downstream of the impeller exit 15B, as discussed above.
  • the apertures 32 have a cavity-side opening 33 and a main flow passage side opening 34 (also referred to herein as an "impeller-side opening” 34), and the aperture axes 32A are radially inwardly angled with respect to the central longitudinal axis 11 in a direction extending from the main flow passage side opening 34 to the cavity side opening 33.
  • a meridional plane such as shown in Fig.
  • the cavity side opening 33 is disposed radially inward relative to the main flow passage side opening 34. Additionally, the impeller-side opening 34 is located radially outward from the impeller exit 15B, relative to the longitudinal central axis 11. The cavity-side opening 33, which is disposed radially inward from the impeller-side opening 34, is therefore located closer to the central axis 11 than the impeller-side opening 34.
  • the aperture axes 32A may be radially outwardly angled with respect to the central longitudinal axis 11, such that the main flow passage side opening 34 may be radially outward relative to the cavity side opening 33.
  • the main flow passage side opening 34 is located radially outward relative to the impeller exit 15B.
  • the cavity side opening 33 may also be located radially outward relative to the impeller exit 15B, such as in the depicted embodiments, or in alternate embodiments, the cavity side opening 33 may be located radially inward relative to the impeller exit 15B.
  • the radial angle ⁇ of the aperture axes 32A with respect to the central longitudinal axis 11 is -80° ⁇ ⁇ ⁇ 0° or 0° ⁇ ⁇ ⁇ 80°. More particularly, in one embodiment, the radial angle ⁇ is -80° ⁇ ⁇ ⁇ -40° or 40° ⁇ ⁇ ⁇ 80°, and in another embodiment the radial angle ⁇ is -70° ⁇ ⁇ ⁇ -50° or 50° ⁇ ⁇ ⁇ 70°. In a further particular embodiment, the radial angle ⁇ is 45° ⁇ 10°. The radial angle ⁇ may be different in other embodiments, but still excluding about 0° (i.e. 0° ⁇ 5°). While all the apertures 32 have their aperture axis 32A uniformly radially angled with respect to the central longitudinal axis 11 in an embodiment, one or more apertures 32 may be radially angled differently from one or more other apertures 32, in some embodiments.
  • the apertures 32 are tapered in a direction extending from the cavity 30 toward the main flow passage.
  • a cross-sectional area of the cavity side opening 33 may be larger than a cross-sectional area of the main flow passage opening 34, whereby fluid exiting the main flow passage to enter the cavity 30 through the apertures 32 may pass in a divergent passage defined by the apertures 32 to reach the cavity 30.
  • fluid exiting the cavity 30 to re-enter the main flow passage may pass in a convergent passage defined by the apertures 32. This may provide optimal swirl to the downstream diffuser 20 and/or provide better vortical structure which may increase mixing of the fluid exiting the cavity 30 with the fluid of the main flow passage at the impeller exit 15B.
  • the apertures 32 may be tapered in the opposite direction, if desirable.
  • the apertures 32 may have a convergent-divergent shape, such that the apertures 32 may have a choked cross-section, i.e. a cross-sectional area, between the cavity side opening 33 and the main flow passage side opening 34, that is smaller than the cavity side opening 33 and/or the main flow passage side opening 34.
  • the apertures 32 have a conical shape, which may diverge or converge toward the cavity side opening 33, depending on the embodiment.
  • the apertures 32 have a conical angle ⁇ that is -20° ⁇ ⁇ ⁇ 0° or 0° ⁇ ⁇ ⁇ 20°.
  • the conical angle ⁇ is 10° ⁇ 5°.
  • the conical angle ⁇ may be different in other embodiments.
  • the apertures 32 may thus be radially angled (i.e. radially inwardly or radially outwardly angled relative to the central longitudinal axis 11) and tapered toward the cavity side opening 33 or the main flow passage side opening 34.
  • the apertures 32 may or may not be all equally tapered, depending on the embodiment.
  • the apertures may have many suitable cross-section shapes.
  • a diameter D1 of the apertures 32 at the cavity side opening 33 may be greater than a diameter D2 of the apertures 32 at the main flow passage side opening.
  • these diameters D1 and D2 may be the measure of the maximum transversal dimension of the openings 33, 34.
  • the apertures 32 may have other shapes, such as a rectangular cross-sectional shape.
  • the apertures 32 have a constant cross-section shape, though the cross-section shape may vary from the cavity side opening 33 and the main flow passage side opening 34 in other embodiments.
  • all the apertures 32 have a uniform cross-section shape in an embodiment, one or more apertures 32 may have different cross-section shapes than one or more other apertures 32, in some embodiments.
  • the apertures 32 may be circumferentially angled relative to a plane normal to the central longitudinal axis 11.
  • the cavity side opening 33 and the main flow passage side opening 34 of the apertures 32 are circumferentially offset relative to each other.
  • Such plane may correspond to the plane A-A shown in Fig. 3A taken transversally to the longitudinal axis 11.
  • the circumferential angle ⁇ may also be defined as the angle relative to a line tangent to the impeller exit 15B radius (perpendicular to the central longitudinal axis 11). For instance, in an embodiment as shown in Fig.
  • a circumferential angle ⁇ of the aperture axes 32A relative to the plane normal to the central longitudinal axis 11 is -80° ⁇ ⁇ ⁇ 0° or 0° ⁇ ⁇ ⁇ 80°. More particularly, in an embodiment, the circumferential angle ⁇ is -80° ⁇ ⁇ ⁇ -40° or 40° ⁇ ⁇ ⁇ 80°, and in some cases the circumferential angle ⁇ is -70° ⁇ ⁇ ⁇ -50° or 50° ⁇ ⁇ ⁇ 70°. In a particular embodiment, the circumferential angle ⁇ is 45° ⁇ 10°. The circumferential angle ⁇ may be different in other embodiments.
  • apertures 32 While all the apertures 32 have their aperture axis 32A uniformly circumferentially angled relative to the plane normal to the central longitudinal axis 11 in an embodiment, one or more apertures 32 may be circumferentially angled differently from one or more other apertures 32, in some embodiments.
  • the apertures 32 have length L defined from the cavity side opening 33 and the main flow passage side opening 34 taken along the aperture axes 32A. In an embodiment, a ratio of the length L of the apertures 32 over the diameter D1 of the cavity side opening 33 is ⁇ 1. While all the apertures 32 have a uniform length L in an embodiment, one or more apertures 32 may have a greater length than one or more other apertures 32, in some embodiments.
  • the series of apertures 32 may also take the form of a series of elongated slots. This is shown in Fig. 6 , for instance.
  • the elongated slots have an arcuate cross-section shape, though other cross-section shapes may be contemplated.
  • the arcuate cross-section shaped slots have their radius oriented toward the central longitudinal axis 11, such as shown.
  • the arcuate cross-section shape may also have their radius oriented differently, for instance away from the central longitudinal axis 11, in other embodiments.
  • both arrangements may provide better alignment of the flow exiting the cavity 30 with the flow downstream of the impeller exit 15B and upstream the diffuser passages leading toward the combustor 16 or another compressor stage when compared with impeller 15 and diffuser 20 assembly(ies) with a single, non-angled, circumferential slot between the cavity 30 and the main flow passage downstream of the impeller 15, adjacent the tips of the impeller blades 15A, as may be provided in some cases, for instance.
  • This may advantageously improve the cavity influence on downstream diffuser stall margin in some embodiments.
  • annular slot extending circumferentially about the impeller exit 15B, instead of having the series of apertures 32 described above.
  • the annular slot would be radially angled and the above description in this regard would also be applicable to this embodiment.
  • the annular slot may also have other characteristics described above with respect to other embodiments, including the characteristics described with respect to the tapered shape of the apertures 32 and location of the apertures 32 within the centrifugal compressor 14A.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP20163432.6A 2019-03-15 2020-03-16 Laufradspitzenhohlraum Pending EP3708804A1 (de)

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US16/354,292 US11143201B2 (en) 2019-03-15 2019-03-15 Impeller tip cavity

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EP3708804A1 true EP3708804A1 (de) 2020-09-16

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Publication number Priority date Publication date Assignee Title
US11143201B2 (en) 2019-03-15 2021-10-12 Pratt & Whitney Canada Corp. Impeller tip cavity
WO2020231798A1 (en) * 2019-05-14 2020-11-19 Carrier Corporation Centrifugal compressor including diffuser pressure equalization feature
US11268536B1 (en) * 2020-09-08 2022-03-08 Pratt & Whitney Canada Corp. Impeller exducer cavity with flow recirculation

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